JPH01257787A - Compressor - Google Patents

Abstract

PURPOSE:To feed a proper quantity of lubricating oil even at the time of low speed rotation and low oil level by providing a bypass extending upward from a pump chamber and an oil feeding passage connecting the pump chamber to the bottom end of the oil passage of a rotary shaft. CONSTITUTION:A pump chamber 37 and the bottom end of the oil passage 39 of a rotary shaft 5 are connected by an oil feeding passage 38. A disk 33 for giving centrifugal force to lubricating oil is installed on the lower end of the rotary shaft 5, and a pump chamber 37 is formed with a casing 34 surrounding this disk and a bottom cover 36 having an oil suction port 68. A bypass pipe 40 is provided from this pump chamber 37 to the position of the lubricating oil feeding port of an upper bearing 7. Thereby, a high head can be obtained as an oil feeding pump by means of the centrifugal force generated by the rotation of the disk 33.

Description

Detailed Description of the Invention [Field of Industrial Application] The present invention relates to a compressor, which is used for example in refrigerators, air conditioners, etc., and which has a compression element housed in a closed container. The present invention relates to a compressor that can supply an appropriate amount of lubricating oil to each sliding part from the time of rotation to the time of high-speed rotation.

[Prior Art] A conventional compressor in which a compressor element is housed in a closed container has an oil supply mechanism for supplying lubricating oil to each sliding part, for example, as disclosed in Japanese Patent Application Laid-Open No. 61-197. As described in Japanese Patent No. 187591, a plug is fitted into the center hole at the lower end of the rotating shaft, and the lubricating oil is sucked up by the lift created by the rotation of the plug and supplied to each sliding part. What has been done is known. In addition, as described in Japanese Patent Application Laid-Open No. 61-157788, a lubricating piston is attached to the lower part of the rotating shaft, and the piston draws up lubricating oil with the lift generated by eccentrically rotating inside the lubricating cylinder. Also known are those that supply each sliding portion.

[Problems to be Solved by the Invention] Among the above-mentioned conventional techniques, the one described in Japanese Patent Application Laid-Open No. 187591/1983 is difficult to solve when the rotation speed of the compressor becomes low (i.e., the compressor is a rotation speed control type compressor). ), or lubricating oil stored in a sealed container enters the refrigeration cycle.
1 and the curved surface decreases, the head is insufficient,
There was a problem in that it was impossible to supply an appropriate amount of lubricating oil to each sliding part.

Moreover, the one described in Japanese Patent Application Laid-Open No. 157788/1988 is
By increasing the rotation diameter of the oil supply screw I~, it is possible to obtain sufficient head even when the rotation speed of the compressor is low or the oil level is low, but if the rotation speed of the compressor is If it is too high, the head will be too high and more lubricating oil will be supplied than necessary. As a result, the lubricating oil released from the rotating shaft causes the rotation of the rotating shaft and the electric power! It is stirred by the lower balance way 1 provided at the bottom of the IJ machine rotor. The compressed refrigerant scum is carried into the refrigeration cycle, resulting in a significant drop in oil level.
There has been a problem in that the efficiency of the refrigeration pile is reduced due to the circulation of lubricating oil within the refrigeration cycle. The present invention improves the problems of the prior art described above, and can supply an appropriate amount of lubricating oil to each sliding part even during low speed rotation and low oil level, and even during high speed rotation. The object of the present invention is to provide a compressor that causes less lubricating oil to leak into the refrigeration cycle and that causes less oil level drop.

[Means for Solving the Problems] The composition of the compressor according to the present invention for solving the second problem is that an electric motor consisting of a stator and a rotor, and a crank are placed in a closed container that also serves as a lubricating oil reservoir. a rotating shaft that rotates together with the rotor, which has an oil passage that opens to the lower end; a cylinder that has a groove for sliding the vane; and a cylinder that is fitted in the crank and rotates eccentrically along the inside of the cylinder. Laura.

A vane that reciprocates in the groove of the cylinder while in contact with this roller and partitions the inside of the cylinder into a suction chamber and a compression chamber, an upper bearing and a lower bearing that serve as the bearing of the rotating shaft and the side wall of the cylinder. and a compression element disposed below the electric motor, a disk attached to the lower end of the rotating shaft capable of applying centrifugal force to the lubricating oil, and a casing surrounding the disk. and a lower cover which forms a pump chamber with the casing and has an oil suction port open; a bypass passage extending in two directions from the pump chamber and opening near the lower end surface of the upper bearing; It has an oil supply passage that communicates the pump chamber and the lower end of the oil passage of the rotating shaft.

More specifically, a disk that applies centrifugal force to the lubricating oil is attached to the lower end of the rotating shaft, a casing surrounding this disk and a lower cover with an oil suction port form a pump chamber, and the upper bearing is lubricated from this pump chamber. A bypass pipe is provided up to the oil filler port.

[Operation] The centrifugal force generated by the rotation of the disk attached to the lower end of the rotating shaft increases the pressure of the lubricating oil in the pump chamber, resulting in a high lift as an oil supply pump.

Therefore, even at low speed rotation or low oil level,
An appropriate amount of lubricating oil is supplied to each sliding part of the compression element.

Also, as the rotation speed of the compressor increases and the capacity of the oil supply pump increases, the amount of oil flowing into the bypass passage increases.
The increase in the amount of oil supplied to the sliding parts is small, and the amount of lubricating oil stirred by the rotation of the rotating shaft or lower balance weight is reduced. Therefore, there is less lubricating oil flowing out of the refrigeration cycle, and there is less deterioration of the curved surface.

[Example] The present invention will be explained below using examples.

FIG. 1 is a longitudinal sectional view of a compressor according to a first embodiment of the present invention, and FIG. 2 is a sectional view taken along the line A-A in FIG.

The outline of this compressor will be explained using FIG. 1. In this compressor, a stator 3
1. The rotor 1 has an electric motor M consisting of a rotor 13, a crank 4, and an oil passage 39 opening to the lower end.
3. A rotating shaft that rotates together with 5. Cylinder 1 with a groove for vane sliding; Roller 3 fitted into the crank 4 and rotating eccentrically along the inside of the cylinder 1; reciprocating within the groove of the cylinder 1 while in contact with the roller 3;
A vane 2 that partitions the inside of the cylinder 1 into a suction chamber and a compression chamber.
an upper bearing 7 that serves as both a bearing for the rotating shaft 5 and a side wall of the cylinder 1; It is equipped with a lower bearing 8 and a compression element C disposed below the electric motor M, and has a lubricating oil 2
A disk 33 is attached to the lower end of the rotating shaft 5 and has a semicircular balance hole 3S in the eccentric direction of the crank 4. a casing 34 surrounding the casing 33;
4 to form a pump chamber 37 and a lower cover 36 with an oil suction port 68 opened. This compressor has a bypass pipe 40 that is a bypass path extending to the lower end surface, and an oil supply path 38 that communicates the pump chamber 37 with the lower end of the oil passage 39 of the rotating shaft 5.

This will be explained in detail below.

In FIG. 1, 1 is a cylinder of a compressor, 3 is a roller that rotates eccentrically within this cylinder 1, 4 is a crank that gives rotation to this roller 3, and this crank 4 is
It is integrated with the rotating shaft 5.

M is an electric motor, and stator 31. The rotor 13 is fixed to one end of the rotating shaft 5. Main bearings 9.7 and 8 are located at the upper and lower ends of the cylinder 1, respectively, and support the rotating shaft 5. These are an upper bearing and a lower bearing having a sub-bearing 10. A vane 2 is pushed from behind by a spring 6 and reciprocates while contacting an eccentrically rotating roller 3, partitioning the inside of the cylinder 1 into a compression chamber and a suction chamber. 14 is a discharge valve, 15 is this discharge valve 14
It is a stopper. 16 is a side plate that forms a silencer 17 with the lower bearing 8. 32 is the oil level of the lubricating oil 20 stored in the lower part of the closed container 27.

33 is a disk which is fixed to the lower end of the rotating shaft 5 and is larger in diameter than the rotating shaft 5 and is a rotor of the spiral oil supply pump P; 63 is a spiral blade attached to the disk 33;
68 is an oil suction port provided in this lower cover 36;
38 is a bypass pipe that extends from the pump chamber 37 to the lower end surface of the upper bearing 7, and 38 is a bypass pipe that is attached to the lower cover 36 and
7 and an oil passage 39 bored in the rotating shaft 5 , 41 is a sub-bearing oil supply path bored in the rotating shaft 5 and opens to the sub-bearing 10 , 43 is a sub-bearing oil supply path that communicates with an oil passage 39 bored in the rotating shaft 5 Drill and main bearing 9
A main bearing oil supply passage 42 is a crank oil supply passage bored in the crank 4 in the opposite direction to the eccentric direction. This is a gas discharge port. And the main bearing 9. Secondary bearing 1
0 is provided with an oil groove that can guide lubricating oil upward and downward as the rotating shaft 5 rotates.

Reference numeral 35 denotes a balance hole drilled semicircularly in the direction of the crank 4 of the disc 33, and the imbalance of the crank 4 is eliminated by the lower paran weight 28 attached to the lower part of the rotor 13 and this balance hole 35.

The operation of the compressor configured as above will be explained.

When the electric motor M is operated, the rotating shaft 5 fixed to the rotor 13
rotates, and the crank 4 rotates the roller 3.
rotates eccentrically within the cylinder 2.

The refrigerant sucked into the compressor is compressed by changing the volume of a compression chamber partitioned by vanes 2 that reciprocate while in contact with rollers 3.

The compressed refrigerant gas is discharged from the discharge valve]4 to the silencer]
7, from where it passes through a discharge passage (not shown) and is discharged into a sealed container 27. And the discharge pipe 4
7 and sent to the refrigeration cycle.

This is performed together with the refrigerant compression operation. The operation of the spiral oil supply pump P will be explained. The lubricating oil 20 stored in the lower part of the closed container 27 is sucked into the pump chamber 37 through the oil suction port 68 by the spiral blades 63 of the disk 33 that rotates together with the rotating shaft 5 . As a result, the pump chamber 3
7 becomes high, and part of the lubricating oil 20 flows into the oil supply path 38.
The oil is then sent to the oil passage 39 of the rotating shaft 5. The main bearing supply path 43 of this rotating shaft 5. Sub-bearing oil supply path 4].

Crank oil supply path 42 is reached, and the main bearing 9° and the secondary bearing 10. Crank 4. Lubricating oil is supplied to each sliding portion of the roller 3. The lubricating oil 20 supplied to the main bearing 9 is sent to one end by the oil groove, lubricates it, and then is discharged into the closed container 27. The lubricating oil 20 supplied to the sub-bearing “O” is
After being sent downward through the oil groove and lubricated, the lower bearing 8
It is discharged to the lower part of the sealed container 27 from the sub-bearing outlet 45 provided in the.

The lubricating oil 20 supplied to the crank 4 is
The crank oil is sent downward through an oil groove provided in the crankshaft 40 to lubricate it, and then is discharged from the crank oil outlet 46 into the sealed container 27. Further, excess lubricating oil 20 that is supplied into the oil passage 39 and does not contribute to the lubrication of each sliding part is removed from the gas discharge port 44.
is released into the closed container 27. Even if the lubricating oil 20 contains dregs, the dregs are separated from the lubricating oil by the centrifugal force in the oil passage 39 and collected at the shaft center, and are discharged from the gas discharge port 44, so that the gas is not dissipated. There is no flow to the sliding parts, and proper lubrication is achieved.

In this way, the lubricating oil is supplied to each sliding part, but when the lift of the pump chamber 37 reaches the lower surface of the -1-bearing 7, the lubricating oil 20 is supplied from the open end of the bypass pipe 40. It is released into the closed container 27.

For this reason, the height of the curved surface inside the oil passage 39 is set at the height of the bus pass pipe.
The height is the sum of the lift applied to the lubricating oil 20 in the oil passage 39 by the centrifugal force generated by the rotation of the rotating shaft 5 at the other end. Therefore, the oil level in the oil passage 39 is between the main bearing supply path 43 and the gas discharge port 44, and the amount of lubricating oil 20 flowing out from the gas discharge port 44 into the closed container 27 is extremely small.

According to the embodiment described above, there are the following effects.

The spiral blades 63 attached to the disk 33, which has a diameter larger than the diameter of the 00 rotary shaft 5, provide a high lift in the pump chamber 37. Even when the oil level 32 is low, a sufficient lift can be obtained.

Since the bypass pipe 40 extending from the pump chamber 37 to the lower surface of the upper bearing 7 is provided, excessive lubricating oil is not supplied to the oil passage 39 even when the rotation speed of the compressor is high. The amount of lubricating oil 20 discharged from gas discharge port 44 is small, and the amount of lubricating oil stirred by rotation of rotary shaft 5 and lower balance ways 1 to 28 is small. Therefore, -12 = less curved surface reduction, and less lubricating oil flowing into the refrigeration cycle.

Q. As mentioned above, @ improves the reliability of the compressor.
It also improves the efficiency of the refrigeration cycle.

In this embodiment, the upper end opening of the bus pass pipe 40 is -1
- The lower end surface position of the bearing 7 is set at the lowest operating speed of the compressor, and the main bearing oil supply path 43 is moved by the lift given to the lubricating oil in the oil passage 39 by the rotation of the rotating shaft. The same effect can be obtained if the position is lower than or higher than the gas discharge port 44 by the lift given to the lubricating oil in the oil passage 39 by the rotation of the rotating shaft at the maximum rotation speed. It is something that plays.

Other embodiments will be described below.

FIG. 3 is a longitudinal sectional view of a compressor according to a second embodiment of the invention.

In FIG. 3, parts having the same numbers as those in FIGS. 1 and 2 indicate the same parts and perform similar operations. And 48 is
This is a shielding plate fixed to the upper bearing 7, facing the open 1'' end of the upper part of the bypass pipe 40, and covering it without contacting it.

In the compressor configured in this manner, when the rotary shaft 5 rotates and the lubricating oil 20 is released from the bypass pipe 40 due to high head, the lubricating oil 20 hits the shielding plate 48 and the closed container 2
Return to the bottom of 7.

According to the second embodiment described below, the same effects as the first embodiment can be achieved, and 1. Even if the rotational speed of the compressor increases and more lubricating oil is released from the bypass pipe 40, the lubricating oil is blocked by the shielding plate 48 and will not be released to the upper part of the compressor. Therefore, there is an advantage that even less lubricating oil flows into the refrigeration cycle.

FIG. 4 is a longitudinal sectional view of a compressor according to a third embodiment of the present invention.

In FIG. 4, parts with the same numbers as in FIGS. 1 and 2 [W] indicate the same parts and perform similar operations. And 40
A is from the pump chamber 37 to the side plate]6. Lower bearing8. A bypass passage 40a passing through the cylinder 1, and a bypass discharge port 40 extending from the upper end of the bypass passage 40a to the outside of the cylinder 1.
This is a bypass path consisting of b.

In the compressor configured in this manner, when the rotating shaft 5 rotates and the pressure inside the pump chamber 37 increases, a portion of the lubricating oil flows from the bypass passage 4.0a to the bypass discharge port 4.0a. Ob
and is discharged into the sealed container 27. At this time, since the lower end surface of the upper bearing 7 is located at the upper end of the bypass flow path 40a, the lower end surface of the upper bearing 7 serves as a shield plate, and the lubricating oil 20 is not released to the upper part of the compressor.

According to the third embodiment described above, it is possible to provide the same effects as the second embodiment and also to provide an inexpensive compressor since there is no need to specially provide the bypass pipe 4o and the shield plate 48. There are advantages.

FIG. 5 is a longitudinal sectional view of a compressor according to a fourth embodiment of the present invention.

In FIG. 5 and 13, parts having the same numbers as those in FIGS. 1, 2, and 4 indicate the same parts and perform similar operations. 50 is cylinder 1. The oil return 51 is formed by penetrating the lower bearing 8, communicating with the bypass passage 40a at one end of the cylinder 1'', and releasing the other into the closed container 27 at the lower end position of the lower bearing 8. Airtight container 2 from the 1st end
This is a gas suction port that communicates with the inside of the gas tank 7.

In the compressor configured in this way, the disc 33 rotates together with the rotating shaft 5, and the lubricating oil 2 is supplied from the bypass path 4-Oa.
When 0 is released, most of it passes through the oil source 50,
The lubricating oil 20 returns from the lower end of the lower bearing 8 into the sealed container 27, and the remaining lubricating oil 20 returns into the sealed container from the gas suction port 51. Normally, the oil level 32 is above the lower end of the lower bearing 8, so the oil return 5
The lubricating oil 20 returning from zero is released into the lubricating oil 20 stored at the bottom of the closed container 27. When the disc 33 rotates at a low speed, the gas suction port 51 opens into the gas in the closed container 27, so that the siphon effect caused by the oil return 50 does not occur. Therefore, even at low rotations, the upper bearing 7
The lift to the lower end is ensured, and lubricating oil 20 is supplied to each sliding part of the compression element C.

According to the fourth embodiment described above, the bypass flow path 40
Since most of the lubricating oil 20 released to a is released back into the lubricating oil, in addition to the effect of the third embodiment, the ripples on the oil surface are reduced, and the ripples cause the lubricating oil to scatter on nine curved surfaces. It has the advantage of being reduced or reduced.

[Effects of the Invention] As explained in detail above, according to the present invention, an appropriate amount of lubricating oil can be supplied to each sliding part even during low speed rotation and low oil level, and even when rotating at high speed. Also, it is possible to provide a compressor in which lubricating oil leaks less into the refrigeration cycle and the oil level decreases less.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal cross-sectional view of a compressor according to a first embodiment of the present invention, and FIG. 2 is a cross-sectional view taken along the line A-A in FIG.
3 is a longitudinal sectional view of a compressor according to a second embodiment of the present invention, FIG. 4 is a longitudinal sectional view of a compressor according to a third embodiment of the present invention, and FIG. 5 is a longitudinal sectional view of a compressor according to a third embodiment of the present invention. FIG. 7 is a longitudinal cross-sectional view of a compressor according to a fourth embodiment of the invention. ],...Cylinder, 2...Vane, 3...Roller, 4...
Crank, 5, rotating shaft, 7, upper bearing, 8, lower bearing, 13
...Rotor, 27..Airtight container, 31..Stator,
33... Disc, 34... Casing, 36... Lower cover, 37. Pump chamber, 38... Oil supply path, 39 Oil passage, 4o. Bypass pipe, 68... Oil suction port, C. Compression. Element, M... Electric motor, P... Spiral oil pump.

Claims (1)

[Scope of Claims] 1. An electric motor consisting of a stator and a rotor and a crank are housed in a closed container that also serves as a lubricating oil reservoir, and an oil passage opening to the lower end is provided, and the motor rotates integrally with the rotor. a rotating shaft, a cylinder with a groove for sliding the vane, a roller fitted in the crank and rotating eccentrically along the inside of the cylinder, reciprocating within the groove of the cylinder while in contact with the roller, The motor includes a vane that partitions the interior into a suction chamber and a compression chamber, an upper bearing and a lower bearing that serve as a bearing for the rotating shaft and a side wall of the cylinder, and a compression element disposed below the electric motor. In a compressor, a pump chamber is formed by a disk attached to the lower end of a rotating shaft that can apply centrifugal force to lubricating oil, a casing surrounding this disk, and an oil suction port. an oil supply pump comprising a lower cover; a bypass passage extending upward from the pump chamber and opening near the lower end surface of the upper bearing; and an oil supply passage communicating the pump chamber and the lower end of the oil passage of the rotating shaft. A compressor characterized by: 2. The compressor according to claim 1, wherein the bypass path is a bypass pipe attached to the casing. 3. The compressor according to claim 2, wherein a shielding plate is attached to the upper bearing so as to face the open end of the bypass pipe. 4. A patent claim characterized in that the bypass path is a bus path path that includes a bypass path that passes from the pump chamber through the lower bearing and the cylinder, and a bypass discharge port that extends from the end of the bus path path to the outside of the cylinder. The compressor according to item 1.